Thermally powered diaphragm pump system for heat transfer

ABSTRACT

A pneumatic diaphragm pump system shown embodied in a thermally powered refrigeration system with means for heat pumping with a high coefficient of performance while using any of several safe and non-toxic refrigerants. The pump system is driven by pressurized gaseous power fluid through a cycle in which in two embodiments an ejector salvages energy from the adiabatically expanding gaseous fluid in a compartment bounded by a pneumatic diaphragm. Means is provided for cyclic storing of energy and preheating any liquid returned to the gaseous fluid power source.

United States Patent Schlichtig [54] THERMALLY POWERED DIAPHRAGM PUMP SYSTEM FOR HEAT TRANSFER [72] Inventor: Ralph C. Schlichtig, 11212 S. 3rd,

Seattle, Wash. 98168 [22] Filed: June 1, 1971 [21] Appl. No.: 148,723

[ 1 Oct. 24, 1972 3/1964 Tucker ..62/467X 1/1967 Schlichtig ..62/500 Primary Examiner-William J. Wye Attorneyl(enneth W. Thomas [57] ABSTRACT A pneumatic diaphragm pump system shown embodied in a thermally powered refrigeration system with means for heat pumping with a high coefficient of performance while using any of several safe and nontoxic refrigerants. The pump system is driven by pressurized gaseous power fluid through a cycle in which in two embodiments an ejector salvages energy from the adiabatically expanding gaseous fluid in a com- [56] References cued partment bounded by a pneumatic diaphragm, Means UNITED STATES PATENTS is provided for cyclic storing of energy and preheating any liquid returned to the gaseous fluid power source. 2,986,907 6/1961 Hoop ..62/51O 2,991,632 7/1961 Rogers ..62/498 18 Claims, 18 Drawing Figures BOILER /Z 60 #5117 aux/64 M PATENTEDUBT24 I 12 3.699.779

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W qw/y/ THERMALLY POWERED DIAPHRAGM PUMP SYSTEM FOR HEAT TRANSFER This invention relates to a thermally powered diaphragm pump system as applied to a heat transfer system such as a refrigeration system or a heat pump.

In general, this invention is basically a gas or vapor driven heat transfer system that can efficiently pump gas or vapor, for example refrigerant vapor. This ability to pump a vapor is highly desirable in the case of a thermally powered air conditioning system, as the power fluid can then have a much higher boiling point and a much higher critical temperature point than that of the refrigerant fluid being pumped, but without the problems and limitations inherent in mixing the two fluids, such as take place in prior art absorption type air conditioning systems. In addition, a common linear ejector used alone as a vapor powered pump is mechanically inefficient, and is often unstable unless the pressure of the power vapor is accurately con-- trolled as a function of the varying discharge or condenser pressure. A simple prior art diaphragm system used alone as a heat transfer system can maintain separation of gaseous power fluid of a higher boiling point power fluid and of a lower boiling point refrigerant fluid, but here again the mechanical efficiency is low because the energy of expansion of high pressure power vapor in the diaphragm compartment cavity cannot be recovered satisfactorily.

This invention incorporates a double diaphragm unit as a vapor powered pump which provides separation of the higher boiling point power vapor and the lower boiling point refrigerant vapor. In two embodiments of this invention an efficient and versatile ejector as described in U. S. Pat. No. 3,215,088 is associated with two diaphragm pump units in such a cycle that the ejector salvages power from adiabatically expanding power vapor in one diaphragm power vapor compartment to adiabatically compress refrigerant vapor in a diaphragm refrigerant vapor compartment. In a third embodiment of this invention momentum means is provided to assist adiabatic expansion of power vapor in a diaphragm power vapor compartment to help compress refrigerant vapor in a diaphragm refrigerant vapor compartment. In addition, there is means to salvage heat from power vapor to preheat power liquid being delivered to a boiler.

Therefore, an object of this invention is to provide an efficient and relatively inexpensive vapor pump system that can be driven by a wide variety of gaseous fluids.

Another object of this invention is to provide a heat transfer system and heat pump system that can operate directly from steam.

A further object of this invention is to provide an efficient diaphragm type pump system for air conditioning or heat pump systems in which there is a flexibility in choice of safe and nonflammable fluorocarbons to be used as the working substances in the system.

Still another object of this invention is to provide a thermally powered heat transfer system that can easily be reversed for heat pumping.

Another object of this invention is to provide a thermally powered heat transfer system in which the boiler temperature need not be excessively high so as to cause decomposition of the power fluid and corrosion within the boiler.

A further object of this invention is to provide an air conditioning or heat pump system in which the evaporator and/or condenser can be placed at some distance from the remaining power portion of the system.

Another object of this invention is to provide a thermally'powered air conditioning or heat pump system without employing such components as rectifiers and analyzers that add considerable amounts of liquid to liquid heat exchange.

A still further object of this invention is to provide in a thermally powered heat transfer system means for separating the power fluid circuit from the refrigerant fluid circuit so that it becomes easily practical to maintain the proper and safe amount of power fluid in the boiler of the heat transfer system.

Still another object of this invention is to provide an air conditioning or heat pump system that is dependable and easy to service and that has quick response to cooling and heating demand.

A further object of this invention is to provide an air conditioning or heat pump system having convenient evaporator pressures and still have boiler pressures held within maximum values allowed by boiler codes.

Other objects of this invention will become apparent from the following description when taken in conjunction with the accompanying drawings in which:

FIGS. 1A through 1F are schematic diagrams of one embodiment of this invention in which the six time phases of operation for a complete cycle of operation are illustrated for a simple diaphragm pump type of refrigerating or air conditioning system in which an ejector cooperates with a pair of diaphragm pump units in which sequencing valve means is provided to produce the desired cycle of operation.

FIGS. 2a through 2f are schematic diagrams of another embodiment of this invention in which the six time phases of operation for a complete cycle of operation are illustrated for a diaphragm pump type of heat pump in which an ejector cooperates with a pair of diaphragm pump units and with sequencing valve means to produce the desired cycle of operation in which means is also provided for transferring heat from the expanded and exhausted power vapor to liquid power fluid being delivered to the boiler of the heat pump in order to preheat the liquid power fluid.

FIGS. 3a through 30 are schematic diagrams of still another embodiment of this invention in which the three time phases of operation for a complete cycle of operation are illustrated for a diaphragm pump type of heat pump in which the diaphragm pump means is provided with a liquid column of sufficient inertia to store energy during a portion of the cycle of operation.

FIG. 4 is a schematic diagram of a part of the heat pump shown in FIGS. 2a through 2f, which part includes the means for condensing and reevaporating the refrigerant fluid, the means for condensing the vaporized power fluid and the heating and cooling selector valve in which such valve is shown in this figure as set in the heating mode instead of in the cooling mode as is illustrated in FIGS. 2a through 2f.

FIG. 5 is a schematic diagram of a part of the heat pump shown in FIGS. 3a through 3c, which part includes the means for condensing and reevaporating the refrigerant fluid, the means for condensing the vaporized power fluid and the heating and cooling valve in which such valve is shown in this figure as set in the heating mode instead of in the cooling mode as is illustrated in FIGS. 3a through 3c.

FIG. 6 is a partial section view detailing the unidirectional by-pass means of FIGS. 3a through 30.

Referring to FIGS. la through If there is shown the six time phases of operation for one complete cycle of operation of a thermally powered refrigerating or air conditioning system 10 illustrating one embodiment of the teachings of this invention in which working substances such as dichlorodifluoromethane (R-12) for the refrigerant fluid and dichlorotetrafluoroethane (R414) for the power fluid are utilized. In general, the power fluid should have sufficiently higher boiling point than the refrigerant fluid that the vapor pressure of the power fluid at the temperature within the power fluid condenser is somewhat less than the vapor pressure of the refrigerant fluid within the refrigerant evaporator. Under typical operating conditions the normal boiling point of the power fluid should be approximately 70 higher than the normal boiling point of the refrigerant fluid that is used as a working substance in the air conditioning system 10. However, other suitable working substances other than R-12 and R-114 could be utilized in the air conditioning system 10 provided the choice of working substances is made such that a satisfactory difference in boiling points is provided. Of course, a given boiling point for a given working substance can be achieved by mixing two liquids of unequal boiling points. For example, one can mix R-114 and trichloromonofluoromethane (R-ll) to obtain a power fluid having a boiling point somewhat higher than that of R-114. One can choose water as the power fluid if a refrigerant of appropriate boiling point is selected such as trichlorotrifluoroethane (R-ll3). However, it is usually preferred to use fluorocarbons for both working substances as it is desirable that the vapor pressure of neither of the working substances multiplies too rapidly with increase in temperature.

In general, the air conditioning system 10 includes a boiler 12 for vaporizing power fluid disposed within the boiler 12; a heat source 13 for the boiler 12; an air finned refrigerant evaporator 14 for reevaporating liquid refrigerant fluid; an air finned refrigerant condenser 16 for condensing and liquefying refrigerant vapor; conduit means 18 for delivering refrigerant at a regulated rate from the refrigerant condenser 16 to the refrigerant evaporator 14; an air finned power fluid condenser 20 for condensing and liquefying power vapor; diaphragm pump means 22 responsive to the pressure energy of the vaporized power fluid from the boiler 12 and including two diaphragm pump units 24 and 26, the diaphragm pump unit 24 including a flexible diaphragm 28 separating the enclosure of the diaphragm pump unit 24 into a power vapor compartment 30 and a refrigerant vapor compartment 32 each .of which compartments 30 and 32 is bounded by the diaphragm 28 and a portion of the enclosure of the diaphragm pump unit 24, and the diaphragm pump unit 26 including a flexible diaphragm 34 separating the enclosure of the diaphragm pump unit 26 into a power vapor compartment 36 and a refrigerant vapor compartment 38 each of which compartments 36 and 38 is bounded by the diaphragm 34 and a portion of the enclosure of the diaphragm pump unit 26; a centrifugal type ejector 40, such as illustrated in U.S. Pat. No. 3,215,088, including a discharge 42, a primary inlet 44 for receiving vaporized power fluid from the boiler 12 through a conduit 46 which includes a solenoid controlled valve 48 which selectively permits or prevents a flow of vaporized power fluid from the boiler 12 to the primary inlet 44 of the ejector 40, and a secondary inlet 50 for receiving expanded vaporized power fluid from the power vapor compartment 36 of the diaphragm pump unit 26 through conduits 52 and 53; and sequencing valve means 54 for controlling the mode of operation of the diaphragm pump units 24 and 26. In practice, the internal volume of the enclosure of the diaphragm pump unit 24 should be substantially equal to the internal volume of the diaphragm pump unit 26. Therefore, the maximum internal volume of the power vapor compartment 36 is substantially equal to. the maximum internal volume of the refrigerant vapor compartment 32 and the maximum internal volume of the power vapor compartment 30 is substantially equal to the maximum internal volume of the refrigerant vapor compartment 38.

The sequencing valve means 54 of FIGS. 1a through If is interconnected with the ejector 40 by means of the conduit 52, a conduit 56, conduit means 58, and with the diaphragm pump units 24 and 26 by means of conduits 53 and 60, and with the power fluid condenser 20 by means of a conduit 64. The sequencing valve means 54 includes three rotary type valves 66, 68 and 70, each of which has three operating positions. The rotary valves 66, 68 and 70 include rotors 72, 74 and 76 respectively, which are driven by a motor and cam combination (not shown) to position the particular rotors 72, 74 and 76 to form continuity between certain associated conduits including conduits 78 and 80 as will be explained more fully hereinafter. Whenever the solidly shown portions of the rotors 72, 74 or 76, or whenever any of the other solidly shown portions of any of the other rotors of any of the sequencing valve means hereinafter described, are shown covering the entrance or exit of a conduit it is to be understood that no power fluid can flow into or out of such covered entrance or exit of such conduit.

In order to interconnect the refrigerant vapor compartments 32 and 38 of the diaphragm pump units 24 and 26 respectively with the refrigerant evaporator 14 and with the refrigerant condenser 16, conduits 82,84, 86 and 88 are provided. Intake check valves 90 and 92 are provided for permitting refrigerant vapor to flow from the conduit 86 to conduits 84 and 82 respectively, but for preventing refrigerant vapor flow in the reverse sense. On the other hand, exhaust check valves 94 and 96 permit flow of compressed refrigerant vapor respectively from conduits 84 and 82 to the conduit 88, but prevent flow of refrigerant vapor in the reverse sense.

For the purpose of delivering liquid power fluid to the boiler 12 a conduit means 98 including a pump 100 is provided. In particular, the pump 100 pumps condensed liquid power fluid from the power fluid condenser 20 through the conduit means 98 to the boiler 12.

The operation of the air conditioning system 10 of FIGS. la through If will now be described. As hereinbefore mentioned each complete cycle of operation has six phases, each time phase of which is determined by the position of the sequencing valve means 54. The schematic diagrams in each of the FIGS. 1a through If illustrate respectively the positioning of the valve components and the direction of fluid flow for the particular time phase of operation being illustrated. It is to be noted that in each of the time phases of operation hereinafter described with reference to this embodiment and with reference to all subsequent embodiments, each diaphragm will have an associated arrow to indicate its direction of movement during the illustrated time phase; the absence of an arrow in any case indicates that the diaphragm is substantially not in motion during the illustrated time phase.

Referring to FIG. 1a, which illustrates the first of the six time phases of operation, the solenoid operated valve 48 is in the open position and the sequencing valve means 54 is so positioned as to permit the flow of vaporized power fluid from the boiler 12 through the conduit 46, the primary inlet 44 of the ejector 40, the discharge 42 of the ejector 40, the conduit means 58, the rotary valve 70 and the conduit 60 to fill the power vapor compartment 30 of the diaphragm pump unit 24 with vaporized power fluid at a pressure sufficient to overcome the pressure opposition of the diaphragm 28 as caused by the back pressure in the refrigerant condenser 16, to thereby effect a movement of the diaphragm 28 in a direction as shown by the arrow and expell refrigerant vapor from the refrigerant vapor compartment 32 and force such compressed refrigerant vapor through the conduit 82, the check valve 96 and the conduit 88 and into the refrigerant condenser 16 where heat of condensation of the refrigerant vapor is liberated and the refrigerant is condensed to a liquid. Liquefied refrigerant flows from the refrigerant condenser 16 to the refrigerant evaporator 14 in a restricted and controlled manner through the conduit means 18 during this time phase of operation and all subsequent time phases of operation. During this same time phase of operation as shown in FIG. la the secondary inlet 50 of the ejector 40 is connected through the conduit 52, the rotary valve 66, and the conduit 53 to the power vapor compartment 36 of the diaphragm pump unit 26 to permit substantially adiabatic expansion of the power vapor enclosed within the power vapor compartment 36 with resultant decrease in pressure therein and flow of the expanded power vapor from the power vapor compartment 36 through the conduit 53, the rotary valve 66, the conduit 52, the ejector 40, the conduit means 58, the rotary valve 70 and the conduit 60 into the power vapor compartment 30 of the diaphragm pump unit 24. This flow of expanded power vapor from the power vapor compartment 36 of the diaphragm pump unit 26, when the pressure within the power vapor compartment 36 is relatively lower than the pressure within the receiving power vapor compartment 30 of the diaphragm pump unit 24, and into the receiving power vapor compartment 30 is made possible by the pumping action of the ejector 40.

Referring to FIG. 1b there is illustrated the positioning of the various valve components and the fluid flow for the air conditioning system for the second time phase of operation. During this time phase of operation the solenoid operated valve 48 is closed and the sequencing valve means 54 is positioned to permit the flow of expanded vaporized power fluid from the power vapor compartment 36 of the diaphragm pump unit 26 through the conduit 53, the rotary valve 66, the conduit 78, the rotary valve 68 and the conduit 64 to the power fluid condenser 20 where the vaporized power fluid is condensed to a liquid. Since the pressure within the power vapor compartment 36 of the diaphragm pump unit 26 was decreased during the first time phase of operation, the amount of vaporized power fluid remaining in the power vapor compartment 36 is minimized, which in turn minimizes the amount of heat that must be rejected by the power fluid on condensing in the power fluid condenser 20. This in turn increases the coefficient of performance of the air conditioning system 10.

The positioning of the sequencing valve means 54 illustrated in FIG. 1b permits the pressure of the evaporated refrigerant vapor within the refrigerant evaporator 14 to force refrigerant vapor through the conduit 86, the check valve and the conduit 84 to fill the refrigerant vapor compartment 38 of the diaphragm pump unit 26 with refrigerant vapor to thus effect a movement of the diaphragm 34 in the direction indicated by the arrow to thereby displace expanded power vapor within the power vapor compartment 36 through the conduit 53 and eventually into the power fluid condenser 20. The liquid condensed power fluid is continuously being pumped by the pump during all of the time phases of operation from the power fluid condenser 20 through the conduit means 98 to the boiler 12.

Now referring to FIG. 1c there is illustrated the positioning of the various valve components and the fluid flow for the air conditioning system 10 for the third time phase of operation in which substantially adiabatic expansion of power vapor takes place in the power vapor compartment 30 of the diaphragm pump unit 24 and substantially adiabatic compression of refrigerant vapor takes place in the refrigerant vapor compartment 38 of the diaphragm pump unit 26. In the description of the various embodiments of this invention it is assumed that the diaphragm pump units such as the units 24 and 26 are sufficiently insulated from ambient heat sources that we can speak of substantially adiabatic expansion of vapor and of substantially adiabatic compression of vapor. It is also common in cases of adiabatic expansion that useful work is derived at the expense of heat stored in the adiabatically expanding vapor itself. This useful work shows up in substantially adiabatically compressing refrigerant vapor within another compartment. During this third time phase of operation the solenoid operated valve 48 is closed and the sequencing valve means 54 is .set to permit substantially adiabatic expansion of the vaporized power fluid within the power vapor compartment 30 of the diaphragm pump unit 24 to cause a flow of vaporized power fluid through the conduit 60, the rotary valve 70, the conduit 80, the rotary valve 68, the conduit 78, the rotary valve 66 and the conduit 53 into the power vapor compartment 36 of the diaphragm pump unit 26 to deflect the diaphragm 34 in the direction indicated by the arrow and thus substantially adiabatically compress refrigerant vapor within the refrigerant vapor compartment 38 of the diaphragm pump unit 26. 

1. A thermally powered heat transfer system using as working substances a power fluid and a refrigerant fluid having a relatively lower boiling point than the power fluid and comprising the following connected components to form the heat transfer system: means for vaporizing the power fluid; means for condensing and for reevaporating the refrigerant fluid; diaphragm pump means having a power vapor compartment means and a refrigerant vapor compartment means and being responsive to the pressure energy of the vaporized power fluid; means for condensing the vaporized power fluid; means including sequencing valve means for controlling the mode of operation of said diaphragm pump means by permitting a flow of vaporized power fluid from said means for vaporizing the power fluid to the power vapor compartment means of said diaphragm pump means during a time phase of operation when said diaphragm pump means is offering sufficient pressure opposition to the vaporized power fluid flowing into the power vapor compartment means of said diaphragm pump means that at another time phase of operation as determined by said sequencing valve means substantially adiabatic expansion of such vaporized power fluid in such power vapor compartment means will yield work sufficient to substantially adiabatically compress refrigerant vapor in the refrigerant vapor compartment means of said diaphragm pump means, and by permitting during still another time phase of operation a flow of expanded vaporized power fluid from the power vapor compartment means of said diaphragm pump means to said means for condensing the vaporized power fluid, such flow of expanded vaporized power fluid being due to the pressure of evaporated refrigerant vapor flowing from said means for condensing and for reevaporating the refrigerant fluid to the refrigerant vapor compartment means of said diaphragm pump means; means for delivering the substantially adiabatically compressed refrigerant vapor from the refrigerant vapor compartment means of said diaphragm pump means to said means for condensing and for reevaporating the refrigerant fluid; and means for delivering liquid power fluid to said means for vaporizing the power fluid.
 2. The heat transfer system of claim 1 in which the maximum internal volume of the power vapor compartment means of said diaphragm pump means is substantially equal to the maximum internal volume of the refrigerant vapor compartment means of said diaphragm pump means.
 3. The heat transfer system of claim 1 in which at least the refrigerant fluid is a fluorocarbon.
 4. The heat transfer system of claim 1 in which said means for condensing and for reevaporating the refrigerant fluid includes an outdoor heat exchanger which is constructed to function as either a refrigerant evaporator or as a refrigerant condenser, and an indoor heat exchanger which is constructed to function as either a refrigerant condenser or as a refrigerant evaporator; an ambient insulated heat exchanger disposed in heat exchange relationship with said means for condensing the vaporized power fluid; a heating and cooling selector valve for effecting a flow of the compressed refrigerant vapor from the refrigerant vapor compartment means of said diaphragm pump means to said outdoor heat exchanger when said heating and cooling selector valve is set for the cooling mode of operation for the heat transfer system, and for effecting a flow of the compressed refrigerant vapor from the refrigerant vapor compartment means of said diaphragm pump means to said indoor heat exchanger when said heating and cooling selector valve is set for the heating mode of operation for the heat transfer system; means for delivering condensed refrigerant from said outdoor heat exchanger to said ambient insulated heAt exchanger when said heating and cooling selector valve is set in the cooling mode of operation for the heat transfer system; means for delivering condensed refrigerant from said indoor heat exchanger to said ambient insulated heat exchanger when said heating and cooling selector valve is set in the heating mode of operation for the heat transfer system; and means for selectively delivering refrigerant vapor from said ambient insulated heat exchanger to either said outdoor heat exchanger or to said indoor heat exchanger when the particular said outdoor heat exchanger or said indoor heat exchanger is functioning as a condenser.
 5. The heat transfer system of claim 1 in which said diaphragm pump means includes a pair of diaphragm units in which the power vapor compartment means is associated with one of said diaphragm units and the refrigerant vapor compartment means is associated with the other of said diaphragm units.
 6. The heat transfer system of claim 5 in which means is provided for interconnecting said pair of diaphragm units with a confined column of liquid having inertia and velocity during at least a portion of the cycle of operation of the heat transfer system.
 7. A thermally powered heat transfer system using as working substances a power fluid and a refrigerant fluid having a relatively lower boiling point than the power fluid and comprising the following connected to form the heat transfer system: means for vaporizing the power fluid; means for condensing and for reevaporating the refrigerant fluid; diaphragm pump means responsive to the pressure energy of the vaporized power fluid and including at least two diaphragm units, one of said two diaphragm units having a diaphragm, a power vapor compartment disposed on one side of the diaphragm and a liquid filled compartment disposed on the opposite side of the diaphragm, and the other of said two diaphragm units having a diaphragm, a refrigerant vapor compartment disposed on one side of such latter diaphragm and a liquid filled compartment disposed on the opposite side of such latter diaphragm, and conduit means enclosing a liquid column and being interconnected between the two liquid filled compartments associated with said two diaphragm units to thus interconnect said diaphragms with liquid having a predetermined inertia; means for condensing the vaporized power fluid; means including sequencing valve means for controlling the mode of operation of said diaphragm pump means by permitting during a time phase of operation a flow of vaporized power fluid from said means for vaporizing the power fluid to the power vapor compartment of said diaphragm pump means to effect an acceleration of said liquid column from the liquid filled compartment associated with said one of said two diaphragm units toward the liquid filled compartment associated with said other of said two diaphragm units, and by preventing during the next time phase of operation the flow of vaporized power fluid to the power vapor compartment of said diaphragm pump means during which latter time phase of operation the vaporized power fluid within the power vapor compartment of said diaphragm pump means expands substantially adiabatically to thus substantially adiabatically compress refrigerant vapor in the refrigerant vapor compartment of said diaphragm pump means and expell such compressed refrigerant vapor into said means for condensing and for reevaporating the refrigerant fluid, and by permitting during still another time phase of operation a flow of expanded vaporized power fluid from the power vapor compartment of said diaphragm pump means to said means for condensing the vaporized power fluid, such flow of expanded vaporized power fluid being due to the pressure of evaporated refrigerant vapor flowing from said means for condensing and for reevaporating the refrigerant fluid to the refrigerant vapor compartment of said diaphragm pump means; and means for delivering liquid power fluid to said means for vaporizing the power fluid.
 8. The heat trAnsfer system of claim 7 in which said diaphragm pump means includes a unidirectional by-pass for the liquid associated with said diaphragm pump means so that during said still another time phase of operation the flow path for the liquid flowing from the liquid filled compartment associated with the refrigerant vapor compartment to the liquid filled compartment associated with the power vapor compartment is shortened thus reducing the inertia of such flowing liquid.
 9. The heat transfer system of claim 7 in which the meniscus of the liquid in the liquid filled compartment associated with the refrigerant vapor compartment functions as the diaphragm separating such liquid filled compartment from such refrigerant vapor compartment.
 10. The heat transfer system of claim 7 in which said means for condensing and for reevaporating the refrigerant fluid includes an outdoor heat exchanger which is constructed to function as either a refrigerant evaporator or as a refrigerant condenser and an indoor heat exchanger which is constructed to function as either a refrigerant condenser or as a refrigerant evaporator; an ambient insulated heat exchanger disposed in heat exchange relationship with said means for condensing the vaporized power fluid; a heating and cooling selector valve for effecting a flow of the expelled compressed refrigerant vapor from the refrigerant vapor compartment of said diaphragm pump means to said outdoor heat exchanger when said heating and cooling selector valve is set in the cooling mode of operation for the heat transfer system and for effecting a flow of the expelled compressed refrigerant vapor from the refrigerant vapor compartment of said diaphragm pump means to said indoor heat exchanger when said heating and cooling selector valve is set for the heating mode of operation for the heat transfer system; means for delivering condensed refrigerant from said outdoor heat exchanger to said ambient insulated heat exchanger when said heating and cooling selector valve is set in the cooling mode of operation for the heat transfer system; means for delivering condensed refrigerant from said indoor heat exchanger to said ambient insulated heat exchanger when said heating and cooling selector valve is set in the heating mode of operation for the heat transfer system; and means for selectively delivering refrigerant vapor from said ambient insulated heat exchanger to either said outdoor heat exchanger or to said indoor heat exchanger when the particular said outdoor heat exchanger or said indoor heat exchanger is functioning as a condenser.
 11. The heat transfer system of claim 7 in which said means for delivering liquid power fluid to said means for vaporizing the power fluid includes a condensing heat exchanger for preheating such liquid power fluid by means of power vapor received from said power vapor compartment during the first portion of said next time phase of operation in which initial substantially adiabatic expansion of the power vapor within said power vapor compartment takes place.
 12. A thermally powered heat transfer system using as working substances a power fluid and a refrigerant fluid having a relatively lower boiling point than the power fluid and comprising the following connected to form the heat transfer system: means for vaporizing the power fluid; means for condensing and for reevaporating the refrigerant fluid; diaphragm pump means responsive to the pressure energy of the vaporized power fluid and including at least two diaphragm pump units each of said two diaphragm pump units having a diaphragm, a power vapor compartment on one side of the diaphragm and a refrigerant vapor compartment on the opposite side of the diaphragm; means for condensing the vaporized power fluid; an ejector for receiving vaporized power fluid from said means for vaporizing the power fluid; means including sequencing valve means for controlling the mode of operation of said diaphragm pump means by permitting during a time phase of operation a flow of vaporiZed power fluid from said means for vaporizing the power fluid and through said ejector to fill the power vapor compartment of one of said two diaphragm pump units with vaporized power fluid to overcome the pressure opposition of the diaphragm of said one of said two diaphragm pump units as caused by the back pressure in a condensing portion of said means for condensing and for reevaporating the refrigerant fluid to thereby expell refrigerant vapor from the refrigerant vapor compartment of said one of said two diaphragm pump units into said means for condensing and for reevaporating the refrigerant fluid, and by permitting during another time phase of operation substantially adiabatic expansion of such vaporized power fluid in the power vapor compartment of said one of said two diaphragm pump units to substantially adiabatically compress refrigerant vapor in the refrigerant vapor compartment of the other of said two diaphragm pump units, and by permitting during still another time phase of operation a flow of expanded vaporized power fluid from the power vapor compartment of said one of said two diaphragm pump units to said means for condensing the vaporized power fluid, such flow of expanded vaporized power fluid being due to the pressure of evaporated refrigerant vapor flowing from said means for condensing and reevaporating the refrigerant fluid to thus fill the refrigerant vapor compartment of said one of said two diaphragm pump units; and means for delivering liquid power fluid to said means for vaporizing the power fluid.
 13. The heat transfer system of claim 12 in which means is provided for heat exchanging the expanded vaporized power fluid flowing from the power vapor compartment of said one of said two diaphragm pump units to said means for condensing the vaporized power fluid with at least a portion of the liquid power fluid being delivered to said means for vaporizing the power fluid to thereby preheat such liquid power fluid by cooling the expanded vaporized power fluid before delivery to said means for condensing the vaporized power fluid.
 14. The heat transfer system of claim 12 in which said means for condensing and for reevaporating the refrigerant fluid includes an outdoor heat exchanger which is constructed to function as either a refrigerant evaporator or as a refrigerant condenser, and an indoor heat exchanger which is constructed to function as either a refrigerant condenser or as a refrigerant evaporator; an ambient insulated heat exchanger disposed in heat exchange relationship with said means for condensing the vaporized power fluid; a heating and cooling selector valve for effecting a flow of the expelled refrigerant vapor from the refrigerant vapor compartment of said one of said two diaphragm pump units to said outdoor heat exchanger when said heating and cooling selector valve is set for the cooling mode of operation for the heat transfer system, and for effecting a flow of the expelled refrigerant vapor from the refrigerant vapor compartment of said one of said two diaphragm pump units to said indoor heat exchanger when said heating and cooling selector valve is set for the heating mode of operation for the heat transfer system; means for delivering condensed refrigerant from said outdoor heat exchanger to said ambient insulated heat exchanger when said heating and cooling selector valve is set in the cooling mode of operation for the heat transfer system; means for delivering condensed refrigerant from said indoor heat exchanger to said ambient insulated heat exchanger when said heating and cooling selector valve is set in the heating mode of operation for the heat transfer system; and means for selectively delivering refrigerant vapor from said ambient insulated heat exchanger to either said outdoor heat exchanger or to said indoor heat exchanger when the particular said outdoor heat exchanger or said indoor heat exchanger is functioning as a condenser.
 15. A thermally powered heat transfer system using as working substances a power fluid anD a refrigerant fluid having a relatively lower boiling point than the power fluid and comprising the following connected to form the heat transfer system; means for vaporizing the power fluid; means for condensing and for reevaporating the refrigerant fluid; diaphragm pump means responsive to the pressure energy of the vaporized power fluid and including at least two diaphragm pump units each of which diaphragm pump units having a diaphragm, a power vapor compartment on one side of the diaphragm and a refrigerant vapor compartment on the opposite side of the diaphragm; means for condensing the vaporized power fluid; an ejector including a discharge, a secondary inlet and a primary inlet for receiving vaporized power fluid from said means for vaporizing the power fluid; means including sequencing valve means interconnected with said two diaphragm pump units and with the discharge and with the secondary inlet of said ejector for controlling the mode of operation of said diaphragm pump means by permitting during a time phase of operation a flow of vaporized power fluid from said means for vaporizing the power fluid and through the primary inlet and discharge of said ejector to fill the power vapor compartment of one of said two diaphragm pump units with vaporized power fluid to overcome the pressure opposition of the diaphragm of said one of said two diaphragm pump units as caused by the back pressure in a condensing portion of said means for condensing and for reevaporating the refrigerant fluid, to thereby expell refrigerant vapor from the refrigerant vapor compartment of said one of said two diaphragm pump units into said means for condensing and for reevaporating the refrigerant fluid, and by permitting during the same time phase of operation a flow of power vapor from the power vapor compartment of the other of said two diaphragm pump units to the secondary inlet of said ejector, and by permitting during another time phase of operation substantially adiabatic expansion of such vaporized power fluid in the power vapor compartment of said one of said two diaphragm pump units to substantially adiabatically compress refrigerant vapor in the refrigerant vapor compartment of said other of said two diaphragm pump units, and by permitting during still another time phase of operation a flow of expanded vaporized power fluid from the power vapor compartment of said one of said two diaphragm pump units to said means for condensing the vaporized power fluid, such flow of expanded vaporized power fluid being due to the pressure of evaporated refrigerant vapor flowing from said means for condensing and reevaporating the refrigerant fluid to thus fill the refrigerant vapor compartment of said one of said two diaphragm pump units; and means for delivering liquid power fluid to said means for vaporizing the power fluid.
 16. The heat transfer system of claim 15 in which means is provided for heat exchanging the expanded vaporized power fluid flowing from the power vapor compartment of said one of said two diaphragm pump units to said means for condensing the vaporized power fluid with at least a portion of the liquid power fluid being delivered to said means for vaporizing the power fluid to thereby preheat such liquid power fluid by cooling the expanded vaporized power fluid before delivery to said means for condensing the vaporized power fluid.
 17. The heat transfer system of claim 15 in which said means for condensing and for reevaporating the refrigerant fluid includes an outdoor heat exchanger which is constructed to function as either a refrigerant evaporator or as a refrigerant condenser and an indoor heat exchanger which is constructed to function as either a refrigerant condenser or as a refrigerant evaporator; an ambient insulated heat exchanger disposed in heat exchange relationship with said means for condensing the vaporized power fluid; a heating and cooling selector valve for effecting a flow of the expelled refrigerant vapor from the refrigerant vapor compartment of said onE of said two diaphragm pump units to said outdoor heat exchanger when said heating and cooling selector valve is set for the cooling mode of operation for the heat transfer system and for effecting a flow of the expelled refrigerant vapor from the refrigerant vapor compartment of said one of said two diaphragm pump units into said indoor heat exchanger when said heating and cooling selector valve is set for the heating mode of operation for the heat transfer system; means for delivering condensed refrigerant from said outdoor heat exchanger to said ambient insulated heat exchanger when said heating and cooling selector valve is set in the cooling mode of operation for the heat transfer system; means for delivering condensed refrigerant from said indoor heat exchanger to said ambient insulated heat exchanger when said heating and cooling selector valve is set in the heating mode of operation for the heat transfer system; and means for selectively delivering refrigerant vapor from said ambient insulated heat exchanger to either said outdoor heat exchanger or to said indoor heat exchanger when the particular said outdoor heat exchanger or said indoor heat exchanger is functioning as a condenser.
 18. The heat transfer system of claim 15 in which said means for delivering liquid power fluid to said means for vaporizing the power fluid includes a condensing heat exchanger for preheating such liquid power fluid by means of power vapor received through said sequencing valve means from the power vapor compartment of said other of said two diaphragm pump units during still another time phase of operation in which initial adiabatic expansion of the power vapor within the power vapor compartment of said other of said two diaphragm pump units takes place. 